Chuckless turning machine



pri l5, 1941. G. F. JOHNSON 238,328

CHUCKLESS TURNING MACHINE Filed Deo. 4, 1939 5 sheets-sheet )1 April 15,1941. G. F. JOHNSON CHUCKLESS TURNING MACHINE Filed Dec. 4, 1939 5Sheets-Sheet 2 April 15, 1941. G. F. JOHNSON CHUCKLESS TURNING MACHINE'Filed Deo. 4, 1939 5 sheets-sheet 5 fig.

April 15, 1941- G. F; JOHNSON CHUCKLESS TURNING MACHINE Filed Dec. 4,1959 5. Sheets-Sheet 4 nventor April 15, 1941. G. F. JOHNSON CHUCKLESSTURNING MACHINE Filed Dec. 4, 1959 5 Sheets-Sheet 5 Patented Apr. l5,1941 CHUC'KLESSTURNING MACHINE;

Glen F. Johnson, Detroit, Mich., assignor to Bower Roller BearingCompany, Detroit, Mich., a corporation of Michigan ApplicationDecember4, 1939, Serial No. 307,399

20 Claims.

This` invention relates, in general, to turning machines and, inparticular, to a new and im proved turning machine of the centerless orchuckless type.

One of the objects of this invention is to minimize the number of partsnecessary for a machine of the above class and type and to improve theirinter-relationship so as to maximize their operating efficiencies.

Another object is. to provide a new and improved machine of theY aboveclass and type wherein the mechanism for feeding the work onto thesupport therefor is controlled by the mechanism for holding said work.on said support and for permitting its release therefrom, whereby thepossibility of said work jamming said latter mechanism is eliminated.

Another object is to provide a machine for the purposes hereinafterdescribed with a new and improved work feed mechanism which operatesexclusively in response to the operation of the work holding mechanism.

Another object is to provide a machine for the purposes hereinafterdescribed with a new and improved work holding mechanism which operates,in addition to holding the work in place on its support, to control thework feed mechanism.

Another object is to provide a new and improved tool supportingstructure for a machine capable of supporting a work piece which isreciprocable toward and from the piece along a .pair of rectilinearpaths which are normal to each other and the reciprocation along one ofwhich paths determines and controls the reciprocation along the other ofwhich paths, whereby tool operation is improved and simpliiied over thatat present well known and in practice.

Another object is toprovide a new and improved tool supporting structurefor a machine capable of supporting a work piece which is simpler inconstruction and more efficient in operation than heretofore, readilyand easily adjustable and changeable to meet conditions of varying sizesand types of work pieces, and operable over long periods withoutnecessity for care, attention,` adjustment or repair.

Anothery object is to provide a turning machine with a new and improvedwork discharging mechanism the operation of which depends upon andresponds to the operation of the tool supporting mechanism wherebyjamming between the tool and the nished work, in the removal A ofthelatter from the machine, is impossible and wherein the parts of said ywork discharging mechanism are minimized in number and more efficientlyinter-arranged with respect to each other as well asA with respect tothe parts comprising said tool supporting mechanism.

Another object isv to provide a machine having a tool movablerectilinearly into and out of engagement with the work with a new andimproved mechanism for discharging the finished work from the machinewhich is controlled by the tool movement and operated exclusively by,upon and responsive to the disengagement of the tool and work.

Another object is to provide a new and improved turning machine whichhas. arectilinearly movable tool the 'operation of which is eitherautomatic or manual and the change-over from one to thefother of whichtypes of operation may be made speedily and selectively.

Other objectsvand advantages of the invention will become readilyapparent from a reference to the following specification taken in con-Ajunction with the accompanying drawings of whichv there are ve (5.)sheets andwherein:

Figure 1 is a plan view of the. machine hereinafter described, samebeing shown partly broken away and in section to illustrate more clearlysome of the details of its construction;

Fig. 2 is a longitudinal, vertical section taken along the lines 2-2, inFig. 1 and showing the tool supporting structure of the machine in itsoperative position;

Fig. 3 is an elevational View of the left end of the machine as it isshown in Fig. 1;

Figs, 4, 5, 6 and 7 are sections taken along the lines 4 4, 5 5, 6,-6and 1--1, respectively, in Fig. 2;

Fig. Sis a section taken along the lines 8-8 in Fig. 5;

Fig. 9 is a view similar to- Fig. 2 but showing the tool supportingstructure of the machine in its inoperative position;

Fig. 10 is a section taken along the lines lil-l 0 in Fig. 2;

Fig. 1l is a development of the peripheral surface of the cam fordriving the tool and its supporting structure, said figure showing saidcam and its follower in the same relative positions as they are shown inFigs. 1 and 2 and also showing the pressure roll cam and its follower intheir true positions with respect to each other and to said rst cam andfollower;

Figs. 12 and 13 are sections taken, respectively, along the lines |2--I2and l3-i3 in Figs. 5 and 3;

Figs. 14 and 15 are schematic views, taken 90 apart, of the arrangementof the work and the driving and pressure rollers therefor and showingthe preferred angularity between the shafts carrying said rollers;

Figs. 16 and 17 are sections of unfinished and finished work,respectively for which the machine herein disclosed and hereinafterdescribed may readily be made adaptable;

Figs. 18 and 19 are sections similar to Figs. 16 and 17 but of adifferent type of work which is particularly adapted for the toolsupporting structure in the machine shown in the figures alreadydefined;

Fig. 20 is an elevational view of the working or front end of a modifiedform of tool supporting structure particularly adapted for working thework shown in Fig. 16 into the form shown in Fig. 17; and

Fig. 21 is a view taken longitudinally through the structure shown inFig. 20 and being partly broken away and in section to set forth moreclearly some of the details of its co-nstruction.

The body of the machine shown herein and to be described hereaftercomprises a super-strucvertical wall I2 which has formed thereon ahollow boss I3 extending horizontally from each side thereof. Inadjacency tothe wall I2 there is fixedly mounted to the lower inner wallof the casing II an upstanding bearing support I4 formed with a centralbore I5 in coaxial alignment with the bore in the boss I3 and with abore I6 on each side of said bore I5 and slightly therebelow, the axesof the bores I6 being slightly out of parallelism with each other andwith the axis of said bore I5 for reasons which will presently appear.

In the bore of the hollow boss I3 there is rotatably mounted, withinsuitable bearings provided therefor, a shaft I1 on the outer end ofwhich is keyed for rotation therewith a pulley I8 and on the inner endof which is keyed for rotation therewith a pinion I9, said shaft beingrotatably driven about its axis by means such as a belt inter-engagingsaid pulley and another pulley (not shown) carried on the drive shaft(not shown) of a source of rotary power (not shown) disposed below thecasing II within the base I0. The pinion I9 is in constant,simultaneous, driving mesh with a pair of gears 2| and 22, said gear 2|being keyed to for rotation with a shaft 23 rotatably mounted insuitable bearings provided therefor within one of the bores I6, and saidgear 22 being keyed to for rotation with a shaft 24 rotatably mounted insuitable bearings provided therefor within the other bore I6. An idlershaft 25 is rotatably mounted in suitable bearings provided thereforwithin the bore I5 which is arranged intermediate the bores I6 andslightly thereabove, said shaft having xed to for rotation with the endthereof opposite the end adjacent the boss I3 an annular, cup-shapedbacking member 26, while each of the shafts 23 and 24 has fixed theretofor rotation therewith, slightly ahead of said backing member, aknurled, Workdriving roller 21. The driving rollers 21 and the idlebacking member 26 are so spaced with respect to each other that anannular work piece, which is to be presently described, is supportableupon said rollers and against said backing member With the axis of saidwork piece in alignment with the axis of said backing member.

Above the bearing support I4 within the casing I I there is arranged ahollow boss 28 which is supported for pivotal movement toward and fromsaid support I4 by means of a lever 29 which is integral at one end withsaid boss and pivoted to an interior web 30 of said casing by means of apin 3|. A shaft 32 is rotatably carried within the boss 28 in suitablebearings provided therefor and its axis is slightly out of parallelismwith the axis of the idler shaft 25 and with the non-parallel shafts 23and 24, said shaft 32 xedly carrying on one of its ends for rotationtherewith a gear 33 normally in mesh with the pinion I9 and xedlycarrying on the other of its ends for rotation therewith a knurledpressure roller 34 in normal engagement with the work piece beingsupported by the driving rollers 21 and the backing member 26. With awork piece in place on the rollers 21 and against the backing member 26and with the roller 34 in lowered and pressing position upon the piecethe latter will be rotated by these unidirectionally moving rollers 21and 34 in a direction oppositely thereto and about an axis aligned withthe axis of the shaft 25. As is described in my co-pending application,Serial No. 273,308, filed May 12, 1939, and entitled Method of andapparatus for honing roller bearing cup members, and as is shown inFigs. 14 and 15 herein, the shafts 23, 24 and 32 are preferablyangularized with respect to each other so that the rollers carriedthereon produce a wiping action upon the periphery of the work piecebeing rotated thereby and cause the drawing of said piece into rm con'.tact with the backing member 26.

The lever 29 which is pivoted at 3I and is also an integral part of theboss 28 carrying the pressure roller shaft 32 extends outwardly throughthe rear of the casing II and is pivotally connected at its free end toone end of a connecting rod 35, the other end of said rod beingconnected to a double-acting piston 36 reciprocably mounted within aclosed cylinder block 31 therefor anchored to the base I0 rearwardly ofsaid casing. Connected to the cylinder 31 on opposite sides 'of thepiston 36 is a pair of pipes 38 and 39 which, in turn, communicate withanother pair of pipes 40 and 4I, respectively, leading into a singlesupply pipe 42 connected to a source (not shown) of compressed air,steam or other high pressure uid. Connecting the pipe 38 to the pipe 40and the pipe 39 to the pipe 4I is a pair of pipes 43 and 44respectively, one of which is perforated at one of its end portions andthe other of which is perforated at the end portion thereof oppositesaid first end portion, and each of said pipes 43 and 44 having arrangedthereon a reciprocable sleeve 45. The two sleeves 45 are unitarilymovable along their respective pipes 43 and 44 by means of a fork 46interconnecting same, and it is seen, particularly in Fig. 4, thatmovement of said sleeves in one di` rection along said pipes opens theperforations in one of said pipes to the atmosphere while the per'-forations in the other of said pipes are simultaneously closed to theatmosphere, and that movement of said sleeves along said pipes in theopposite direction effectuates the reverse conditions with respect tothe perforations in said pipes. In other words, looking at Fig. 4, thesleeves 45 are in such position that the perforations in pipe 44 areexposed and the perforations in pipe 43 are covered. This means that theuid pressure in the pipe 4I is dissipated through the perforations inthe pipe 44 and has, therefore, no effect upon Apositively rotated aboutwords, since the gear 49 integral therewith the piston 36 through thepipe' 39, buty that the pressure in the pipel 40 isv transmittedthroughithe closed pipe 43 and the pipe 38 into the cylinder 3'1 toraisesaid piston and thereby actuate the lever 29 about the pin 3| to lowerthe shaft 32 and the pressure roller 34 carried thereon relatively tothe driving rollers 21, as shown in Fig. 4. On the other hand, if thesleeves 45 are moved by the fork 46 toward the left from that positionthereof shown in Fig. 4, the perforations in the pipe 44 will becomecovered and those in the pipe 43 will become exposed, in which event thepressure in the cylinder 31 below the piston 36 and in the pipe 38 willbe dissipated through the exposed perforations in the pipe 43, and thepressure in the pipe 4IV will be transmitted past the closedperforations in the pipe 44, through the pipe 39 and into the upper endof said cylinder to force said piston downwardly and cause the reverseactuation of the lever 29 and theV raising of the shaft 32 and theroller 34 relatively to the rollers 21.

Considering Figs. 4 and 5 the lever-29 has positioned the pressureroller 34 firmly against the work piece to be worked and the gear 33 indriven. engagement with the pinion I9, it will be seen that said workpiece is its axis from no less than three simultaneously existingsources of driving power, namely, the two driving rollers 21 and saidpressure roller 34 which are unidirectionally rotated under the drivingforce of said pinion I9 which is transmitted to the gears 2I and 22 andsaid gear 33. The driving engagement between the pinion I9 and gear 33must, of course, concur with the pressure engagement'between the roller34 but it is clearly not mechanically essential that the pitch diametersof said pinion and said gear be tangent in order that there be a drivingrelationship therebetween. As a matter of fact, though Fig. 4, purelyfor illustrative purposes, shows the above mentioned pitch diameterstangent, a slight spacing therebetween is highly desirable and in nosense detrimental to the driving force of the` pinion I9 with respect tothe gear 33 for it enables the pressure engagement between the rollerv34 and the work piece to be established and maintained. even when theformer is in a worn condition. In other 33 and the roller 34 arcuatelymove unitarily with the lever 29 to interengage said gear with thepinion I9 and said roller with the work piece, and since the movement ofsaid lever isv limited for all practical purposes to the establishmentof a pressure contact between said roller and said work piece, theexistence of a spacing between the pitch diameters of said gear and saidpinion, when said pressure contact is established, permits theself-adjustment f the pressure between said roller and said work pieceunder conditions when said roller is worn or otherwise slightlyundersized.

As shown in Figs. 1, 4 and 7, a support 41 is employed for rigidifyingthe piping assembly previously outlined and this support is rigidlyattached to and extends into the casing II at a position between theperforated or selectively vented pipes 43 and 44, rocably carrying thestem 48 of a cam follower and residing within said casing. The outer endof the stem 43 isk xed to for movement with the fork 46, and telescopedabout said stern between the follower 4.9

momentarily, wherein said support recipf and the work piece,

and` an' abutmentv formed. by the stationary support 41 is a spring 50which tends to` hold said fork', stem and follower in the positionsthereof shown in Fig. 4, or, in other words, to arrange the valve 44-45in open position and the valve 43-45 in closed position,` under whichconditions the pressure on the lower working face of the piston36 holdsthe outer end of the lever 29 in raised position and the shaft 32, gear33 and pressure roller 34 in their lowered, operative positions. It isclear that, when the follower 49 is positioned in opposition to` thespring 50, the valve 44-45 will be closed, the valve 43-45 will be open,the pressure in the cylinder 31 will be acting on the upper Working faceof the piston 36, the outer end of the lever 29 will be lowered, and theshaft-gear-roller 32-33-34 will be raised into inoperative position. Theactuating mechanism for thefollower 49, is to be described presently.

The upper wall of the casing II isv interiorly formed with a pair ofdepending bearing supports 5I 'dispo-sed on opposite sides of the camfollower 49- and supporting, in suitable bearings therefor, a shaft 52which extends in parallelism with the shafts I1 and 25 from one of saidsupports 5I' through the other thereof and then through the wall I2 (seeFig. 2 particularly). A drum 53 is carried on the shaft 52 between thesupports 5I and is rotatable with said shaft, one end of said drum beingadjacent the follower 49 andfixedly carrying at itsv periphery a camhaving a leading end 54, a trailing end 55 and a dwell portion 56therebetween. As will be seen subsequently, the positioning of the cam54- 55-56 relatively to the drum 53, and the arcuate lengths of each ofthe three elements of said cam, are predetermined with respect to othermatters to be discussed, and it sufces to point out at presentthat saidcam engages, depresses and then releases the follower 49 once perrevolution of said drum and' thereby provides the control for the valves43-45 and 44-45 for actuating the piston 36 and governing the operationof the pressure roller 34.

The end of the casing II opposite the end supporting the drum 53 hasstationarily fixed thereto a pair of spaced, internally dependinghangers 51 between which hangers and within which casing there issuspended a second and smaller casing 58 which, as a result, resides inthe neighborhood of the free end of the drum shaft 52, such suspensionof said casing 58, as shown particularly in Fig. 13, being accomplishedby means of a `pin 59 pivotally interconnecting one of said hangers andthe end of saidcasing 58 more remote from said shaft and also by meansof a hollow boss 6I) pivotally interconnecting the other of said hangersand the end of said Vcasing 58 more adjacent said shaft, the axes ofsaid pin and said boss being aligned so that said casing 5B may, underconditions to be explained, be moved thereabout. The boss 6I! rotatablycarries a shaft 6I to the inner end of which shaft there is keyed forrotation therewith a worm wheel 62 and to the outer end of which shaftthere is also keyed for rotation therewith a sprocket 63. In drivenengagement with the sprocket 63 is a chain 64, and driven by said chainthere is another sprocket 65 which is keyed to for rotation with thefree end of the drum shaft 52. The worm wheel 62 on the shaft 6I is inconstant driven mesh with a worm 65 formed on a transverse shaft 6.1which is journaled for rotation about its axis in the front and rearwalls of the tiltable casing 58, and on said shaft 61 forwardly of saidworm 66 there is fixed thereon for rotation therewith a spiral gear 58.In constant driving mesh with the gear 68 there is a spiral 69 mountedfor rotation on and with the inner end of a shaft which projects intoand is rotatably supported by the casing 58 from without the casing Il,the outer portion of said shaft xedly carrying a pulley 1|. About thepulley 1| which is keyed to the shaft 10 and another pulley 12 which iskeyed to the shaft |1 (see Figs. 2 and 3) there is arranged a belt 13which is driven by the rotation of said shaft |1 for rotating said shaft18 when the casing 58 is in its normal position, that is, un-tilted.

It is clear from the foregoing that the shaft 52 which carries the drum53, the rotation of which drum not only controls the lowering andraising of the pressure roller 34 but also has other functions to bepresently described, is rotatably empowered by the rotation of the shaft|1 through the consecutive agency of the shafts :10 and 8| which arecarried by the casing 58 and are, therefore, tiltably movable therewith,the axis of said shaft 6| being the axis of such tiltability. As seen inFig. l, the shaft 6| is well behind the center of the casing 58 whilethe shaft 18 is well ahead of said center so that, if the lower end ofsaid casing is moved rearwardly about the axis of said shaft 6| (whichwould'alsgl be about the axis of the pin 59), said shaft 18 would belowered with respect to the shaft |1 and the result would be thediscontinuance of the driving force of the belt 13 upon the pulley 1|,the drive between the shafts 6I and 52, obviously, not being affected bysuch casing movement. So, toy enable the casing 58 to be moved toeffectuate the above results, the shaft-carrying boss 80 (see Fig. 13),which is pivotally supported on one of the hangers 51 and is xedlyattached to said casing, has formed thereon at its lower end and between:said casing and said hanger a iiange 14 to which is connected the innerend of a rod 15 extending forwardly from said flange through the frontof the casing On the outer end of the rod 15 there is xedly attached ajaw clutch member 18, and freely mounted on said rod between said memberand the front wall of the casing is an opposing and mating jaw clutchmember 11 provided with a handle 18. The normal position for the clutch18-11 is disengagement, that is, when the jaw of the member 16 isdisengaged from the recess provided therefor in the member 11, for, inthis position the rod 15 is outermost and the casing 58, as a result,uppermost and forwardmost and the pulley 1| in driven engagement withthe belt 13. To disengage the pulley 1| from they belt 13, the handle 18on the free clutch member 11 is turned until the jaw on the member 16 isin position for entering the recess in said member 11, whereupon theweight of the casing 58 itself, because of the offset position of theshaft 6| with respect to the center of said casing, will cause saidcasing to move downwardly and rearwardly about said shaft to disengagesaid pulley from said belt and draw said jaw into engagement with saidrecess.

After the shafts 18, 8| and 52 have been disengaged from the drive shaftI 1 by means of the engagement of clutch 16-11, it may be desirable todrive the drum 53 manually. For this reason, the outer end of the :shaft10 has fixedly conmay be rotated `through the agency of said shafts 18and 6| independently of said shaft |1.

A downwardly, transversely extending runway or trough 80 is supportedintermediate its ends by the front wall of the casing Il, the inner andl lower end of said runway residing directly above and in substantiallythe same vertical plane as the front driving roller 21 (see Fig. 5), andsaid runway Vas a whole being open at its top and preferably adjustablein a vertical direction with respect to said casing. The runway 80 isslightly wider than the axial length of a single Work piece, such as aring blank 8|, so as to provide a proper guide therefor into themachine, and is as long as desired so as to support enough pieces toenable the machine to be operated for a reasonable length of timewithout re-lling said runway. Secured to the front wall of the casingIl, slightly above the runway 80, is a bearing 82 in which there isrotatably supported a horizontal pin 83 one end of which is formed witha head 84 and the other end of which carries one end of a lever 85, saidlever rotating with said pin and extending transversely through saidcasing into permanent resting position upon the top of the movable boss28. The head 84 of the pin 83 carries for rotation or oscillationtherewith an escapement member 85 consisting of a body directlyoverlying the runway 88 and slanting in the same direction thereas, saidbody carrying on its under-surface a pair of abutments or stops 81longitudinally spaced in the direction of the length of said runway. Itwill be noted in Fig. 5, wherein the boss 28 is lowered and the pressureroller 34, therefore, in operative position, that the lower stop v81 isin abutment with a front portion of the lowermost blank 8| in the nectedthereto a handle 18 whereby said shaft 52 75 runway 80, therebypreventing further downward movement of said blank. It will beappreciated that the raising of the lever by the raising of the boss 28and pressure roller 34 will move th-e pin 83 and member 8681 about theaxis of said pin and thereby raise the lower stop 81 out of the path ofthe lowermost blank 8| in the trough 88 and lower the upper stop 81 intothe path of the blank 8| next in line, the lowermost blank, therefore,being permitted to roll from said trough onto the driving rollers 21 andthe next blank rolling down into position against the lowered upper stop81 to remain there until the pressure roller 34 is again lowered intooperative position, whereupon the lowered upper stop 81 will be raisedto release the last mentioned blank and the raised lower stop'81 will belowered to prevent said blank from rolling therepast. As shown in Fig.5, the escapement member 88-81 may be vertically adjustable with respectto the casing so as to vary the normal distances between the stops 81and the rolling surface of the runway 80, thereby permitting theaccommodation in said runway at dilferent times of blanks 8| havingdifferent outer diameters. Also, the distance between the axis of thepin 83 and the point of contact between the boss 28 and the lever 85 isseen to be greater than the distance between said axis and the point ofcontact between the lower stop 81 and the lowermost blank 8| in the feedtrough 80, this meaning that the arcuate movement of said lever isgreater than the arcuate movement of said stop so that said blank is notreleased from said stop until after there has been a substantial raisingof said lever.

Referring now particularly to Fig. 8, the rear shaft 24, which is driventhrough the gear 22 by the pinion |9 and carries one of the drivingrollers 21 (the other being carried by the shaft 23 which is drivenbythe gear 2|), is hollow throughout its length and carries therewithina shaft 88 which extends outwardly from both ends of said shaft 24, thatis, from the end carrying the roller 21 and from the end carrying thegear 22, the latt-er corresponding end of said shaft 88 being suitablysupported by the wall |2 of and within the casing On the end of theshaft 88 immediately adjacent the roller 21 on the shaft 24 there isxedly carried for rotation therewith a centrally arranged, double-armedlever the two arms 89a and 89h of which are 180 apart and radiallydisposed with respect to the axis of said shaft 88. The distance (seeFig. 5) from the axis of the shaft 88 to the end of either of theselever arms, at each of which ends there is integrally formed a flange 90extending in the direction of rotation of said shaft as well as inparallelism therewith and toward the plane of the adjacent roller 21, isless than the distance between the axis of said shaft and the nearestpoint on the circumference of the other roller 21 and is greater thanthe distance between the axis of said shaft and the axis of rotation ofthe blank 8| rotated by said rollers, so that rotation of said leverarms with said shaft will cause the flange 90 on either one or the otherof said arms to contact said blank from below and remove same from itsdriving rollers 21 and direct it rearwardly onto a transversely slantingdischarge trough or runway 9| supported by the rear wall of the .casingwith its upper and front end residing slightly above and insubstantially the same vertical plane as the rear roller 21. runways 80and 9|, therefore, serve as a track for the blanks 8| before and afterthe grinding or turning operations thereon and cooperate with therolling surfaces of the rollers 21 to effectuate the continuity of saidtrack, said rollers receiving one of said blanks from said runway 80when the lever 85 is raised but not until the blank already on saidrollers has been worked and removed therefrom onto said runway 9| by theaction of one of the lever arms 89a. or 89h. The cooperation between thelevers 85 and 89a-89b, and the means for effectuating same, are to bediscussed presently.

On the end of the shaft v88 immediately adjacent the wall l2 on the sideof the latter opposite the gear 22 ther-e is keyed thereto for rotationtherewith a sprocket 92 about which is mounted a chain 93, said chainbeing driven by a sprocket 94 keyed to the end of for rotation with astub shaft 95 journalled in a boss 96 (see Fig.. 2) provided therefor onsaid wall below the drum shaft 52 (see Fig, 6). The shaft 95 alsocarries for rotation therewith an annular member 91 formed at itsperiphery with a plurality of radial sockets 98 spaced 90 apart and aconcave, arcuate surface 99 between each pair of adjacent sockets, saidsurfaces having centers of curvature equally spaced from the axis ofsaid shaft and residing on radii centrally between saidv sockets atpoints radially outwardly of said surfaces. For alternately engaging thesockets 98 and surfaces 99 to give to the shaft 95 an interrupted rotarymotion, such as is known as a Geneva motion, there ris provided adriving pin |88 carried on and movable with the side and at theperiphery of an annular disc |0| mounted for rotation on and with thedrum shaft 52 between the wall |2 and the sprocket 65. It will be notedin Fig. 6 that during one revolution of the drum shaft 52 the pin |00 onthe disc |8`| is The i caused to engage one socket 98 and its trailingsurface 99, thereby moving the shaft 95 onequarter revolution, themovement of said shaft 95 being eifectuated entirely by and during theinterengagement of said socket and said pin because the inter-engagementof said pin and said trailing surface creates merely a dwell in themovement of said shaft 95. As usual, the movement of the shaft 95 is notas rapid during the entrance and exit of the pin |00 into and out of thesocket 98 as it is when said pin is well within said socket and actuallydriving the member 91 at that time.

It is evident by now that the interrupted rotation of the shaft 95 isemployed for the purpose of giving to the shaft 88 -a correspondingrotary movement, said shaft 88 being that shaft which carries thework-ejecting lever 8911-8917. This lever, as shown and as described,has two arms 89a and 89h. The member 91, as shown and as described, hasfour sockets 98. The effective diameter of the sprocket 94, as shown, istwice that of the effective diameter of the sprocket 92. Therefore, onerevolution of the drum shaft 52 brings about a quarter-revolution of theshaft 95 and a half-revolution of the shaft 88. In other words, onerevolution of the drum `53 (which causes the lever to raise once and tolower once) causes the lever BSc-89h to move 180 while the shaft 88 isso moving. As shown in Fig. .5, the provision of more than two arms onlever 89a--8'9b would interfere with the blank 8| residing on'therollers 21, while less than two arms would give rise to such a highspeed of work ejection from said rollers as to be unsatisfactory. Also,as shown in Fig. 6, the provision of a greater ratio .than two-to-onebetween the diameters of the sprockets 94 and 92 would be impractical.Therefore, the choice of a double-armed lever, as shown, the choice of atwo-to-one sprocket ratio, as shown, and the choice of a four-socketedmember (91), as shown, are best in view of the results desired, but itis clear that these choices may and will be modified, and suchmodifications are contemplated.

This point in the discussion marks the completion of the description ofthe work supporting section of the machine or apparatus, and a briefresume follows. Power enters the drive shaft |1 through the -belt 20'and pulley I8 and is distributed through the pinion I9 to the gears 2|,22 and .33 and through the pulley 12 and belt 13 to the pulley 1|. Thepreferably non-parallel shafts 23, 24 and 32, which carry the drivingrollers 21 and the pressure roller 34, respectively, are rotated by thegears 2|, 22 and 33, respectively, and the shaft 10, which carries thespiral gear 69, is rotated by the pulley 1|. The rotative power of theshaft 18 i5 transmitted through the gear 69 to the spiral gear '68 onthe transverse shaft 81, from said shaft 61 to the Worm 6B thereon, fromsaid worm to the worm wheel 82 on the shaft 6|, from said shaft 6| tothe sprocket 63 thereon, from said sprocket throughr the chain 64 to thesprocket B5 on the drum shaft 52, from the pin |00 on the disc |0| onsaid shaft 52 to the individual sockets 98 in the member 91 on the shaft95, and from the sprocket 94 on said shaft through the chain 93 to thesprocket 92 on the shaft 88. The drum shaft 52, though rotated with theroller shafts 23, 24 and 32, does so at a much reduced rate because ofthe reduction gearing residing between said shaft 52 and the shaft |1.

The rotation of the drum shaft 52 controls the feeding of the blanks 8|onto the rollers 21 and also the vdischarging of said blanks from saidrollers. To explaini rotation of the shaft 52 causes cooperation betweenthe cam 54-55-56 and the cam follower 48-49, contact between saidfollower and the leading end 54 and dwell portion 56 of said cam closingthe valve 44-'45 and opening the valve 43-45 to raise the pressureroller 34 and permit a blank 8| to roll from the feed trough 80 onto therollers 21 against the backing member 26, and contact between saidfollower and the trailing end 55 of said cam opening said valve 4445 andclosing said valve 43-45 to lower said pressure roller into engagementwith said blank and maintain said engagement until said leading endre-engages said follower upon the next revolution of said shaft. On theother hand, rotation of the shaft 52 causes, for each full revolutionthereof, a quarter-revolution of the shaft 95 and a resultinghalf-revolution of the shaft 88. Since this half-revolution of the shaft88 is for the purpose of ejecting the blank 8| from the rollers 21 intothe discharge trough 9| through the agency of the lower arm 89h of thelever 89a-89b on said shaft, such shaft movement must be eifectuatedwhile the pressure roller 34 is elevated from said rollers 21. Thismeans that care must be taken in the relative positioning of the cam54-55-56 (see Fig. 7), the pin (see Fig. 6) and the lever 89a-89b (seeFig. so that the lower arm 89h of said lever is ready to eject the blank8| from the rollers 21 by about the time the distance between the risingroller 34 and the rear roller 21 is not much greater than the outerdiameter of said blank, for, at this time, said blank may be ejectedfrom said rollers .21 by said lower arm 89h before the next blank 8| inthe trough 80 has begun its downward travel past the rising, lower stop81.

Referring to Fig. 2, the left support 5| and the right end wall of thecasing carry therein the opposite ends of a pair of horizontal,par-allel guide rods I 02 upon which is reciprocably mounted a toolcarrying structure, generally indicated at |03. Structure |03 comprisesa pair of elongated bosses |04 operable fo-r receiving or being receivedby the guides |02 and being integrated by means of the body of saidstructure itself, said bosses being shorter than the distance betweenthe above mentioned support .5| and end wall of casing to allow forreciprocation of said structure therebetween and along said guides, andsaid body being integrally formed at the end thereof adjacent saidsupport 5| with an annular head portion |05 arranged centrally betweenand below said guides and bosses and in alignment with the axis of thebacking member 26 which axis, incidentally, is coincident with the axisof the work when same is being supported by the rollers 21 and 34against said backing member. The annular nature of the head portion |05of the structure |03 enables the fixed connection to the end thereofadjacent the work of a plate |06 in which there is formed a Verticalslot |01 passing through the axis of said portion |05, said slotreceiving the stems of bolts |08 to which is connected a block or headmember |09. Bolts |08 are spaced from each other a distance less thanthe length of the slot |01 so that the block or head member |09 can beselectively moved vertically with respect to the plate |06 for the sakeof adjustment of said block, said plate having secured thereto onopposite verticalsides of said block, and in spaced relation to saidsides, a pair of screw supports ||0, and saidgscrew supports carryingvertically adjustable 4set screws cooperable with said block formaintaining any selectively adjusted position of the latter.

The block or head member |09 of the reciprocable structure |03 isintegrally formed at its front and rear sides With a pair of dependingwalls ||2 the under-surfaces of which are in a single plane which slantsupwardly at an angle of approximately 45 to the horizonta1 and in thegeneral direction of the work supporting structure of the machine (seeFigs. 2 and 9), said under-surfaces of said walls carrying elongatedplates I8 which extend transversely inwardly toward the longitudinalcenter of said block to dei-lne thereabove and therebetween a guidewayfor a T-shaped tool carrier ||4 (see Figs. 7 and 10). It is clearlyshown that the upper surface of the carrier ||4 has the same angle ofinclination as that of the lower surface of the block |09 which formspart of the gui'deway for said carrier, in other words, that saidsurfaces are complementary and movable one relative to the other, ortogether, as the case may be. The inclined undersurface of the block |09is centrally formed with an elongated slot ||5 which extends in thedirection of travel of said block for a distance less than the length ofsaid surface so that the ends of said slot are defined by the body ofsaid block itself, and the inclined upper surface of the carrier |f4supports an upstanding arm H6 which projects into said slot and is incontact with one end of a spring |1 residing in said slot and abuttingat its opposite end the lower end of said slot, said spring therebypermanently urging said carrier in an upward direction relatively tosaid block along the T-shaped guideway in the latter and said arm towardthe upper end of said slot.

As pointed out, the normal position for the carrier ||4 is that whereatthe arm ||6 is in contact with the upper end of the slot ||5 (see Fig.9), that is, when said carrier is uppermost and outermost with respectto the block |09, and in this normal position a longitudinal bore ||f8formed in said carrier will support the shank ||9 of a turning tool |20so that the cutting edge |2| of said tool will be residing above andaxially outwardly from the point occupied by said edge during theturning operation. Since it is not intended to rotate the tool |20, saidtool and itsl shank ||9 are integral with each other and said shank isremovably held in the bore ||8 against inadvertent axial and/or rotarymovements by means of a pair of lock nuts |22 carried within atransverse bore |23 formed directly below the bore ||8 and held againstsaid shank by a bolt |24 (see Fig, 10). Also, since the tool is to belimited to two movements, one a purely axial movement when the block |09and carrier ||4 move together during the movement of the structure 03along the guides |02, and the other a, vertical movement when said blockand said carrier move relatively one to the other, said tool is arrangedso that its cutting edge 2|, which is shaped so as to turn the innerperiphery of the blank 8| shown in Fig. 18 into the surface formation ofthe blank |8| shown in Fig. 19, is positioned substantiallysymmetrically with respect to a vertical plane which passesthrough andincludes the axis of the backing member shaft 25.

The end of the carrier ||4 opposite the end from which the tool |20projects is bifurcated, as at |25, and receives between suchbifurcations,

by means of a transverse pivot pin |26, the inyner end of an elongatedrod |21 the outer end of which projects beyond the opposite end wall ofthe casing and through a plate |28 secured to said wall of said casing,said outer end of said rod being threaded and adjustably receivingthereon a nut |29. The properly adjusted position of the nut |29 withrespect to the rod |21 as well as to the plate |28 is shown in Fig. 2,this figure showing the structure |03 in fully protracted position withrespect to the Work 8| and the resulting protraction and lowering of thecarrier ||4 and engagement of the tool |20 with said work. Theattainment of the positions shown Iin Fig. 2 of the structure |03,carrier ||4 and tool |20 draws the rod .|21 to the left and therebydetermines the proper positioning of the nut |29 thereon, this latterpositio-n being that whereat said nut abuts the plate |28. Asdistinguished from the positioning of the elements shown in Fig. 2,attention is directed to Fig. 9 wherein the structure |03, carrier H4,tool |20 and rod |21 are fully retracted and said carrier and tool arefully raised.

Referring to Fig, 9, the structure |03 is in its retracted position. Inthis position, Ithe rod |21 is idl-e and the carrier I4 is free to beacted upon by the spring ||1 and moved upwardly and out- Wardlyrelatively to the block |09 until the arm ||6 engages the upper end ofthe slot ||5. The positions shown in Fig. 9 of these elements are, aswill be seen, the same directly before the tool |20 is lowered intocontact with the work and directly after said tool has performed itsturning operation thereon. In other words, there is full protraction ofthe carrier ||4 and tool |20 before said carrier is lowered and saidtool positioned on the work and `there is full raising of said tool andsaid carrier before the retraction thereof is commence-d. Leftwardmovement of the structure |03 and carrier ||4 from their positions shownin Fig. 9 is unitary until the stop nut |=29 contacts the plate |28, atwhich time the cutting edge |2| of the tool |20 is directly aboveworking position. Continued protraction of the structure |03 isindividual and in opposition to the spring |1, the .nut |29 preventingany further protraction of the carrier ||4, and this protraction of saidstructure drives said carrier and the tool |20 downwardly because of.the wedging action created between said carrier and the block 09 byAthe inter-engaging inclined surfaces thereof, the result bein-g theinter-engagement of the cutting edge |2| and inner annular surface ofthe blank 8|, as shown in Fig. 2.

Now referring to Fig, 2, and assuming the turning of the blank 8| hasbeen completed, the initial phase of the retraction of the structure |03will be individual with respect to the carrier |4 because of thecompressed state of the spring ||1 and the dwell created or establishedby the spacing between the arm and the upper end of the slot ||5. Inother words, until this spacing has been eliminated by the necessaryamount of retraction of the structure |03, there will be no retractionof the carrier ||4 but there will be a raising thereof, again because ofthe inclination of the surfaces of the block |09 and said carrier.However, when the arm ||6 engages the upper end of the slot ||5, furtherretraction of the structure |03 will cause and be unitary with theretraction of the carrier ||4 into the positions thereof shown in Fig.9. 1 The means for protracting and retracting the tool supportingstructure |03 to obtain the above outlined results consists of a camsurface formed in the periphery of the drum 53 and followed by afollower |30 carried by the upper surface of the head portion |05 ofsaid structure, a development of the surface providing said cam beingshown in Fig. 11. Looking at Figs. 1, 2 and 11 simultaneously, the camsurface on the drum 53 has a run |3| which extends for substantiallythree-fourths of the entire circumferential length of said drum in thedirection of rotation thereof and with a gradual slope toward the rightend (as viewed in Figs. 1 and 2) of said drum. The leading end of therun |3| is headed by a short run |32 more sharply sloped and directedtoward the right end of the drum 53 than said run |3|, and the trailingend of said run |3| is followed by a short run |33 sloped and directedjust as sharply as said run |32 with respect to said run |3| but towardthe left end of said drum, said runs |32 and |33 being interconnected bya non-sloping run |34 and comprising the other fourth of thecircumferential length of said drum. In Figs. 2 and 11, the drum 53 ismomentarily in such position that the trailing end of the run |3| andthe leading end of the run |33 are engaging the follower |30, the tool|29 at this time being in turning position on the blank 8| but ready tobe elevated therefrom. Retraction of the structure |03 and elevation ofthe tool |20 occur during the travel of the run |33 along the follower|30 and such retraction is complete upon the engagement of the leadingend of the run |34 with said follower, as shown in Fig. 9. A dwell inthe movement of the structure |03 exists while the run |34 is inengagement with the follower |3|) and exists until the leading end ofthe run |32 engages said follower. The engagement of the run |32 withthe follower |30 and the duration thereof cause the unitary protractionof the structure |03 and carrier ||4 to the point where the stop nut |29engages the plate |28, whereafter the engagement of the run |3| withsaid follower and the duration thereof cause the further but individualprotraction of said structure 03 and the resulting lowering of saidcarrier. In short, the extent of the run |3| between its leading andtrailing ends represents the period during and after which the tool |20is being and has been lowered from a position directly above therotating surface of the blank 8| into turning position thereon as shownin Fig. 2; the extent of the run |33 between its leading and trailingends represents the period during which the tool is raised from theturned surface of the blank |8| and the entire tool supporting structureis retracted into the position shown in Fig. 9; the extent of the run|34 between its leading and trailing ends represents the period duringwhich the tool supporting structure is perfectly idle (the reason forwhich follows); and, the extent of the run |32 between its leading andtrailing ends represents the period of unitary protraction of thestructure |03 and carrier ||4 during the take-up between the nut |29 andplate |28 immediately prior to the lowering of said carrier by thecontinued protraction of said structure.

As shown in Fig. 11, the run |33 is about to begin its travel along thefollower |30, while at the same time the leading end 54 of the cam54--55-56 is approaching, though spaced from, the follower 49. 'I'hismeans that the tool |20 is about to be raised and the structure |03 isabout to be retracted, but that the valves 44-45 and 43-45 are -toremain open and closed, respectively, until the leading end 54 reachesthe follower 49. The time elapse for the travel of the drum 53 from theposition whereat the follower |30 and the leading end of the run |33 areinterengaged to the position whereat said follower and the trailing endof said run are inter-engaged is approximately the same as the timeelapse for the travel of the cam 54-55-56 from the position thereofshown in Fig. 11 to the position whereat the leading end of the run 56and the follower 49 are inter-engaged. In other words, the raising andretraction of the tool |20 together with the retraction of the toolsupporting structure |03 are completed, or substantially so, before thepressure roller 34 is raised and the worked piece |8| is ejected by oneof the arms 8911-90 or 89b-90. It will be noted that the dwell 56 is ofshorter duration than the dwell |34, which means that thehalf-revolution of the ejector arm is completed before the pressureroller 34 is lowered and that said roller is lowered before theprotraction of the structure |03| |4 is commenced, the tool |20,therefore, oering no resistance to the operations of either saidpressure roller or the lever of which said arm is a part. A

The showing in Figs. 20 and 21 is a modified tool supporting structurewhich may be substituted for the structure supported by the reciprocablehead portion |05 of the structure |03 already described, therebyenabling the machine to perform turning and ash removing operations onroller bearing cups, such as |35, rather than the operations alreadydescribed and relating to ring blanks, such as 8|, out of which suchcups are formed, the operations on the cup which are desired to beperformed being the .turning of the inner front and rear edges and theremoval of the ilash at the larger end of said cup. So, in the bore ofthe head portion |05 there is clamped or Xed for movement therewith ablock |36 having a sloping bore |31 formed therethrough and extendingdownwardly and generally toward the work supporting structure of themachine, said bore |31 having the same purpose as the sloping guidewayformed in the head member |09 already described. In the bore |31 thereis mounted for reciprocation with as well as relatively to the block |36and head portion |05 the stem |38 of a tool carrier |39 extending intoposition between said block |36 and backing member 26. The rod |21,instead of being connected to the carrier 4, is connected to the stem|38 of the carrier |39 so that movement of the latter carrier |39 isidentical to the movement of the former carrier |4, except that thevertical move ment of the carrier |39, during the introduction of itsnon-rotatable tool 220 to the work |35, is upward rather than downward,as is the case with the carrier H4, the tool 220 thereby engaging `thework at an upper point thereon instead of at a lower point, as is thecase with the tool |20. A slot 2|5, a pin 2|6 and a spring 2|1in thestem |38 and block |36 cooperate and function similarly as the slot l5,arm |6 and spring ||1 in the head |09 and carrier ||4 already described.The tool 220 is operable, as shown in Fig. 21, for turning the twoopposite inner, annular edges of the cup |35 into the form 235 shown inFig. 17.

Still referring to Figs. and 21, flash removal is performed by means ofa tool |40 which is carried by a support |4| residing below the carrier|39 and fixed to the head portion |05 and block |36. The tool |40 haspure horizontal movement with the portion |05 and block |36 because anyvertical movement thereof, such as is the case with either the tool |20or tool 220,

is unnecessary. The tool |40 cooperates with the flash on the larger andnearer end of the cup |35 and completely removes same by the time thetool 220 has performed its two operations.

Although the invention has been described with some detail it is notintended that such description is to be definitive of the limits of theinventive idea. The right is reserved to make such changes in thedetails of construction and arrangement of parts as will come within thepurview of the attached claims.

What I claim is:

1. A machine having, a work support, a pressure roller movable towardsaid support for holding a work piece in place thereon and mova- -bleaway therefrom to enable the piece to be removed therefrom, and a feedmechanism for controlling the feeding of the work onto the support andoperable responsive to the movements of said roller. 2. A machinehaving, a work support, a pressure roller movable toward said supportfor holding a work piece in place thereon and movable away therefrom toenable the piece to be removed therefrom, a feed mechanism forcontrolling the feeding of the work onto the support, and meansoperatively interconnecting said mechanism and said roller forcontrolling said mechanism by and in accordance with the movements ofsaid roller.

3. In a machine having a Work support and a tool movable away from thesupport as well as into an operative position on the work, meansoperable while the tool is away from the support for introducing to thesupport a work piece to be worked, means movable into engagement withthe piece for holding the latter on thev support during tool operationand movable out of engagement therewith thereafter, and means controlledby the latter movement of said second means for controlling theoperation of said rst means.

4. In a machine having a work support and a tool movable away from thesupport as well as into an operative position on the work, a reservoirfor work pieces to be operated upon by the tool and having an outlettherefor in communication with the support, a control for restrictingthe discharge of the pieces through said outlet to periods when the toolis away from the support, means operable when the pieces are on thesupport for establishing a, clamping engagement therebetween .duringtool operations and operable for releasing said engagement to enable thedischarge of the pieces from the support, and means effectuated by anddependent upon said releasing operations of said rst means forcontrolling said control.

5. In a machine having a work' support and a tool movable into and outof operative position with respect to work on the support, a supplyreservoir for work pieces to be operated upon by the tool and having anoutlet in communication with the support, a control cooperable with thepieces within said reservoir and being alternately movable in onedirection between predetermined limits therefor to release one of thework pieces through said outlet into the support and in the oppositedirection between said limits to oppose the release of any of theremaining pieces within said reservoir, means movable into engagementwith the released piece on the support to hold the piece in place duringtool operation thereon and movable out of engagement therewith to enablethe removal thereof subsequent to said operation, and means driven by.said first. means to move -said control in said work-releasing directionyuponsaid'workdisengaging movement of said first :means and to move saidcontrol in said release-opposing direction upon said work-engagingmovement of said rst means.

6. In a machine having a work support and a work reservoir with anoutlet therefor in communication with the` support, means operable uponrelease of work through the outlet onto the support for holding thereleased work in position for being worked and for discharging said workfrom the support subsequent to the working thereof, a work-releasingmember associated with the outlet for eiiectuating and inefectuating thelatter with respect to the releasing therethrough of the work within thereservoir onto the support, and means actuated by and dependent upon theoperation of said first means for controlling the operation of vsaidmember.v

7. In a machine having a work support and a supply reservoir for workpieces with an outlet thereinv for thev pieces and in communication withthe support, pressure actuated means operable for alternately exertingpressures in opposite directions toward and lfrom the support, a controlassociated with the outlet andv operable for releasing a work piecetherethrough onto the support during the exertion of said pressure bysaid means away from the v'support and for opposing the release ofanother work piece through the outlet during'the exertion of saidpressure by said means toward the support, and means operated by saidrst means for operating said control..

8. In a machine having a work support, rotatable drive means, meansmovable toward the support and simultaneously into operative engagementwith said first means for rotating and holding work in place on thesupport and movable away from the support and simultaneously out of saidoperative engagement to enable the release from the support of the work,a piston in communication with a source of pressure therefor, a valvefor controlling said pressure to control said piston, and meansinterconnecting said second means and said piston for controlling themovement of said second means.

9. In a machine having a work support, rotatable drive means, meansmovable toward the support and simultaneously into operative engagementwith said first means for rotating and holding work in place on thesupport and movable away from the support and simultaneously out of saidoperative engagement to enable the release from the support of the work,a piston movable in one direction by pressure for moving said secondmeans in one of its directions and movable in another direction bypressure for moving said second means in its other direction, and a pairof valves movable together in one A direction to effectuate the pressurefor moving said piston in one of its directions and to ineifectuate thepressure for moving said pisto-n in its other direction and movabletogether in another direction to-reverse the pressure conditions on saidpiston for moving the latter in its other direction.

10. In a machine having a work support and a work reservoir incommunication therewith, a member movable toward the support for holdingthe work in place thereon and movable away from the support to enablethe removal there- Vfrom of the Work, a pressure actuated piston indriving relationship with said member for moving the latter toward andfrom the support, and means operable responsive to the movement of saidmember for controlling the supply of work from the reservoir to thesupport.

'11. Ina machine having a work support and a work reservoir in:communication therewith, a member movable toward the support for holdingthe work in place thereon and movable away from the support to enablethe removal'therefrom of the work, a pressure actuated piston in drivingrelationship with said member for moving "the latter toward and fromithe support, means operable responsive to thel movement of saidmemberforcontrolling the supply of work from the reservoir to the support, andmeans for controlling the operation of'said piston with respect' to apredetermined relationship between the operations of said member vandsaid rst means.

12. vIn a ymachine having a work support, a

structure comprising, a pair of body 'members unitarily movabletowardrand from the support between predetermined limits of relative adjacencyand remoteness with respect to the support, means operable for extendingthe movement of one of said members relatively to the other Y of l.saidmembers beyond one of said limits, and

means loperable responsive to said extended movement of said rst memberfor moving said second member in apath normal tothe path of saidextended movement.

13. `A machine comprising, a support for a work piece, a. tool for thework piece,'rotatable drive means forsaid tool ,and operable forreciprocating the latter into and out of operative engagement with theWork piece, ejector'means operable for ejecting the work piece from saidsupport, and means driven by said drive means for rotating said ejectormeans in a single direction and intermittently with respect to therotation of said drive means and in accordance with a predeterminedrelationship with respect to the reciprocation of said tool to eject thework piece from said support while said tool and the work piece aredisengaged.

14. A machine comprising, a support for a work piece, a tool for thework piece, drive means continuously rotatable in a single direction andoperable for rectilinearly moving said tool into and out of operativeengagement with the work piece, a shaft rotatably driven by said drivemeans in a single direction, and means carried on said shaft forrotation therewith and operable for ejecting the work piece from saidsupport in response to the disengagement of said tool and the workpiece.

15. A machine comprising, a support for a work piece, a tool for thework piece, drive meansl continuously rotatable in a single directionand operable for rectilinearly moving said tool into and out ofoperative engagement with the work piece, a shaft rotatably driven bysaid drive means in a single direction and intermittently with respectto the rotation thereof, and means carried on said shaft for rotationtherewith and operable for ejecting the work piece from said support inresponse to the disengagement of said tool and the work piece.

16. A machine comprising, a support for a work piece, a tool for theWork piece, drive means continuously rotatable in a single direction andoperable for rectilinearly moving said tool into and out of operativeengagement with the work piece, a shaft having xed thereon for movementtherewith an ejector member operable for eecting the work piece fromsaid support, and means operatively interconnecting said shaft and saiddrive means for providing intermittent, uni-directional rotation of saidshaft lwith respect to the rotation ofsaid drive means to effectuate theejection of the Work piece from said support by said ejector memberwhile said tool is disengaged from the piece. Y

17. `A machine having a support for holding a work piece in placethereon during operative engagement of the piece with a tool and asupport for the tool reciprocable toward and from the piece to en-gageand -disengage the tool therewith comprising, a rotatable camshaftoperatively connected to the tool support for controlling the engagement`and disengagement of :the tool with the piece, a second shaft carryingan ejector member operable for ejectng `the piece from its support, andmeans operatively interconnecting L said shafts for intermittently anduni-directionally rotating said second-shaft relatively rto said -rstshaft .and responsive to the disengagement of the workpiece and saidtool.

1'8. A machine comprising, a rotatable .camshaft operatively connectedto a tool for rectilinearly moving the latter, va drive shaft, a drivingmechanism arranged between said shafts for rotating said rst shaft ybysaid second shaft, and means Aarranged between .said .shafts forineffectuating said second shaft with respect to said first shaft toaccommodate manual operation of said latter shaft through saidmechanism.

19. In a turning machine, a work support comprising, a pair :of shaftssupported for rotation about laterally `spaced axes .and each having adriving element therefor mounted thereon for rotation therewith, arotatable drive member arranged in permanent driving relationship withsaid Aelements for rotating said shafts together, a thirdz shaftsupported for rotation about an axis spaced from said other shafts andhaving a driving element therefor mounted thereon for rotationtherewith, means for unitarily moving said third shaft and its drivingelement toward and away from said first twoshafts to interengage anddisengage said element and said driving member, and a roller carried oneach of said shafts for rotation and movement therewith for rotatablysupporting a work piece therebetween.

20. In a turning machine, a work support comprising, a pair of shaftseach carrying at one of its ends for movement therewith a drivingelement therefor and at the other of its ends for movement therewith awork driving roller, said shafts being supported for rotation aboutlaterally spaced, fixed axes, a rotatable driving member for saidelements and supported in permanent driving engagement therewith, and athird shaft supported for rotation and for movement toward and away fromsaid first two shafts, said third shaft having a third work drivingroller and a third driving element mounted thereon for) rotation andmovement therewith, said third driving element and said third rollerbeing simultaneously engageable with said driving member and a workpiece supported on said rst two rollers, respectively, upon the movementof said third shaft toward said first two shafts to effectuate therotatable driving of said third roller and the exertion of a pressureupon the work piece.

GLEN F. JOHNSON.

